Hydraulic machine



y 23, 1939- E. E. GUINNESS 2,159,941

HYDRAULIC MACHINE Filed Nov. 14, 1954 5 Sheets-Sheet 1 Edwa'rd Ewur! Gunnnass lNvEMT-opZ May 23, 1939. E. E GUINNESS HYDRAULIC MACHINE FiledNov.

14, 1934 5 Sheets-Sheet 2 fdv vm Pd Ewar'i' Guinness \NVENTOE,

May 23, 1939. E. E. GUINNESS HYDRAULIC MACHINE Filed Nov. 14, 1934 5Sheets-Sheet 4 Edward Ewqv-i- Gui in mass \NVENTOL mun/L. LE AT y 1939-E. E. GUINNESS 2,159,941

HYDRAULIC MACHINE Filed Nov. 14, 1934 5 Sheets-Sheet 5 Edward. EuJoH-Guunnes$ 1NvaN'r UNITED STATES PATENT OFFICE HYDRAULIC MACHINE EdwardEwart Guinness, Wolverhampton, England, assignor, by direct and mesneassignments, to Fluvario, Limited, West Bromwich, England, a company ofGreat Britain Application November 14, 1934, Serial No. 752,966

In Great Britain September 11, 1933,

3 Claims.

This invention relates to hydraulic machines, and concerns machines suchas rotary engines, pumps, vane motors, blowers, exhausters or the like,hereinafter referred to and included in the term rotary engine of thekind including stator and rotor members, the latter being adapted for"rotary movement and provided with vanes adapted to co-operate with theadjacent surface of the stator member in creatingthe head of thedelivered fluid, or in applying the fluid energy to the rotor member.

Other objects will become apparent from the '20 2-2 of Figure 1.

Figure 3 is a detail view of the same construction.

Figure 4 is a sectional side elevation of a modified form of pump.Figure 5 is a sectional side elevation on the line 5-5 of Figure 4.

Figure 6 is a sectional end elevation on the line 66 of Figure 9 showingone form of apparatus for the hydraulic transmission of power embodyinga pair of rotary engines constructed in accordance with this invention.

Figure 'I is a plan view of the construction shown in Figure 6.

Figure 8 is a sectional view on the line 88 of Figure 6 with certainportions of 'the apparatus a removed for the sake of clarity.

Figure 9 is a fragmentary side elevation of the same construction withone of the transfer mem bers removed and taken on the line 9-9 of Figure8.

Figure 10 is an inverted plan view of a transfer member of the sameconstruction.

Figure 11 is a perspective view of a portion of a modified form of vaneemployed in this construction.

Figure 12 is a part sectional view corresponding to the right hand sideof Figure 6 showing a modification of the construction illustrated inFigures 6-10.

Figure 13 is a part sectional view on the line l3--l3 of Figure 12.

Figure 14 is a side elevation of the reversing valve shown in Figures 12and 13. s

In the construction illustrated in Figures 1 55 to 3 of the drawings,the pump comprises a stationary casing III, a stator ll mounted slidablytherein, and a rotor I! mounted rotatably upon the casing and disposedwithin the stator.

The casing comprises a hollow cast metal frame l3 of somewhat squareform closed at each side by end plates M of similar shape, one of theseplates having an attachment bracket [5 formed integrally therewith forsecuring the pump in position.

The rotor is' of cylindrical or disc shape and. is formed integrally ateach end with a supporting spindle [6, one of these spindles formingalso a shaft I! for driving the pump.

Each spindle is supported by a bearing [8 of the roller type, housedeach within an annular flange formed as an axial extension of theadjacent end plate of..the casing, and for closing the bearing adjacentthe driving shaft there is provided an annular cover disc l9 secured-toone of the aforesaid annular flanges, this cover disc being formedcentrally with an annular recess containing a suitable oil seal 20 suchas a felt. washer.

The other bearing is closed by a circular cover member 2| secured to thecasing end plate.

For preventing the fluid from entering the bearings, each casing endplate is formed adjacent the rotor with an annular recess in each ofwhich recesses is mounted a sealing ring 22 comprising an annular cage23 of channel section,- shown more clearly in Figure 3, and havingmounted within the channel and adjacent each side thereof a pair ofmetal rings 24, one of said rings having in abutment therewith anannular leatherwasher 25 of L section, including an inwardly extendingflange which is adapted to be maintained by the fluid pressure incontact with the periphery of the spindle I6.

To ensure that the fluid shall urge the leather washer into abutmentwith the spindle, the sealing ring is provided with a fluid divertingstrip 26 of annular form having an inclined edge 21 extending inwardlyinto abutment with the spindle, such edge serving to cut the adjacentfluid vfilm and to divert the fluid into the interior of the sealingring so that it forces the washer 25 into contact with the spindle.

Conveniently, one or more springs 28 of plate form are provided forurging the strip 26 into engagement with the washer 25.

The stator l l is of generally annular form having an interior ofcircular configuration of a diameter somewhat greater than the diameterof the rotor, and opposite sides of the stator are formed with a suctionport and a delivery port 29 and 30 respectively, for supplying anddischarging the fluid to and from the rotor, and these ports are ofrectangular section and arranged diametrically opposite one on each sideof the rotor.

The upper and lower sides 3| of these ports diverge inwardly of the pumpso that these sides are more or less tangential to the periphery of therotor to facilitate the passage of the fluid through the ports.

Formed in the casing frame l3 on opposite sides thereof and adjacent thesuction and delivery ports are suction and delivery passages 32 and 33communicating respectively with these ports. Conveniently the frame I3is provided adjacent each of these passages with a machined face forconnection to suitable suction and delivery pipes not shown on thedrawings.

The exterior of the stator adjacent the aforesaid suction and deliveryports is machined to provide on opposite sides thereof two planeparallel vertical faces 34 which engage slidably corresponding surfacesformed on the interior of the pump casing adjacent the passages thereofto permit of the necessary relative movement between the pump stator androtor.

Thus a limited sliding movement of the stator is permitted in a verticaldirection and perpendicular to the axis of the driving shaft, and thedimensions of the stator are such that when this is slidden its maximumdistance in one direction relative to the rotor, the interior of oneside thereof abuts the periphery of the rotor, while the exterior of theopposite side abuts the adjacent horizontal surface of the casing frameas is evident from Figure 1.

Although the construction illustrated in Figures 1 to 3 comprises arotary pump, it should be understood that such an arrangement can beemployed equally well as a vane motor, the discharge and suction ports30 and 29 then becoming inlet and exhaust ports respectively forsupplying fluid under pressure to the motor and for discharging ittherefrom.

In order to maintain a fluid-tight connection between the engagingsurfaces of the stator and casing adjacent the port 30 which serves toadmit or discharge fluid under pressure to or from the rotor accordingto whether the apparatus is used as a motor or pump, while permittingthe aforesaid sliding movement; the surface 34 of the stator adjacentthe port 30 is formed with a recess 35 extending annularly around theport and having slidably mounted therein an annular sealing member orring 36 which extends continuously and completely around the port.Convenientlv. the ring is formed from metal such as cast iron.phosphor-bronze. or from-leather, and is adapted for engagement with theadjacent surface of the casing.

In order to ensure such engagement. the recess 35 is provided with aplurality of passages 31 extending inwardly of the sta or andcommunicating with the port adjacent the periphery of the rotor, so thatduring the operation of the apparatus as a pump or motor fluid is forcedunder pressure through these passages to urge the sealing member intoengagement with the housing. and there is provided around the port afluid tight-joint which permits the relative movement between the statorand housing to take place.

Similar sealing means is provided adjacent the port 29 to permit of thedirection of movement of the rotor being reversed for short periods ifrequired when the apparatus is employed as a pump, the port 29 servingunder such circumstances to deliver fluid under pressure from the pump.

Similarly, each end face of the stator may be provided with a recessextending annularly therearound and provided with similar sealing ringsarranged in the same manner to provide a fluid-tight connection betweenthe stator and the casing end plates.

Further, the sealing rings may be carried by the casing itself, althoughit is preferred to mount them in the movable member.

The pump rotor I2 is provided with a plurality of peripheral recesses 38extending longitudinally for the full length thereof, and convenientlyan even number; namely, four such recesses are provided arrangedsymmetrically around the periphery of the rotor.

The recesses are of U section, and have each slidably and rotatablymounted therein a vane 39 of cylindrical form extending for the fulllength of the rotor, the arrangement being such that the vanes arecapable of movement in a radial direction and can thus maintain contactwith the interior of the stator during the complete rotation of therotor for various positions of the stator in relation thereto.

To maintain the vanes in contact with the interior of the stator,opposite recesses are connected each by a passage 40 extendingdiametrically through the rotor and each adapted to contain the fluid sothat when the stator is eccentric in relation to the rotor, during theinward movement of one vane consequent on the rotation of the rotor, thevane opposite thereto is forced outwardly of the rotor by the resultantfluid pressure within the opposite recesses and their connecting passageand into contact with the adjacent surface of the stator.

To maintain the fluid pressure within the recesses 38 and connectingpassages 40 during the continued movement of the rotor, the forwardlongitudinal edge 4| of each recess is provided with an inwardlyextending groove 42 adapted to provide communication between theinteriorof the pump and the base of each recess when the vane is in itsoutermost position and during its passage from the suction to thedelivery port.

Conveniently the depth of each groove is such that on further movementof the vane past the delivery port towards the suction port, the inwardmovement thereof closes the communication between the recess and theinterior of the pump and prevents the egress of the fluid.

By the expression forward is meant that side of the recess which is inadvance of the vane in the normal direction of rotation, i. e., thatside thereof which is subject to fluid pressure.

By constructing the vanes of cylindrical form and mounting themrotatably upon the rotor, the contact between the vanes and the adjacentsurface of the stator is purely a rolling one, so that sliding frictionis substantially eliminated and a considerable saving in wear on thevanes and stator results.

Further, by utilising the pressure of the fluid within the pump forforcing the vanes into engagement with the stator surface, the pressureof the vanes on to the surface is substantially constant for allpositions of the stator in relation to the rotor.

In order that the position of the stator in relation to the rotor can becontrolled, the stator is provided at its upper and lower sides with campieces 43 extending outwardly of the adjacent casing through apertures44 provided in the frame thereof.

Adjacent the outer end of each cam piece, the casing is provided with acam 45 adapted for engagement with the cam piece, and each mounted upona suitable spindle 46 extending longitudinally of the pump, and the endsof these spindles may carry levers 41, the free ends of which areconnected by a link 48 of somewhat curved form to provide clearancebetween it and the driving shaft, while the free end of one of thelevers 41 may be connected to a suitable control lever or otheroperating means. 7

The cams are arranged with their apices at 90 in relation to oneanother, so that each cam serves to move the stator in one directiononly.

With a pump constructed as described above, the fluid is sucked inthrough the suction port and discharged through the delivery port, thevolume of fluid delivered being variable by sliding the pump statorrelative to the casing and rotor.

As is evident from the description, the stator can be slidden into aposition of maximum eccentricity in relation to the rotor in which theeffective length of the vanes is at a maximum during their passage fromthe suction to the delivery port, so that for this position of thestator the maximum volume of fluid is delivered during a given rotationof the rotor.

Further, in this position, the periphery of the rotor and vanes engagesthe interior of the stator during movement from a delivery to a suctionport, and the circulation of any fluid around the interior of the statoris prevented. Thus the maximum amount of useful work is done by therotor with the stator in its position of greatest eccentricity.

The volume of fluid delivered by the pump may be decreased by operatingthe control gear to slide the stator from its maximum eccentricity untilits interior is concentric with the periphery of the rotor, in whichposition the pump does not deliver any fluid, the latter being simplycirculated around the interior of the stator.

On further operation of the control gear to slide the stator beyond itsconcentric position, the direction of flow of fluid within the pump isreversed, and fluid may be sucked in through the delivery port andexpelled through the suction ,fport.

Thus, the quantity of fluid delivered from the pump may be variedinfinitely from a maximum to a zero value and vice versa, while inaddition its direction of flow may be reversed if desired.

Such a form of pump may be employed under all circumstances where itisdesired to varythe quantity of the delivered fluid, and may be employedequally well for pumping water, oil or other liquids.

When employed as a vane motor, the mechanical power output of theapparatus is varied by operating the control gear to slide the stator IItransversely of the rotor l2.

In the modified construction illustrated in Figures'4 and 5, the pump isof a form generally similar to the preceding arrangement, but in thisconstruction, the stator II is of built up type comprising a portion 48arranged annularly around the rotor and having an internal diametersomewhat greater than the diameter of the latter member, and thisannular portion is provided at opposite ends with circular end discs 49and 50 disposed adjacent each end of the rotor,

the former disc being formed integrally with the annular portion, andthe latter constructed separately therefrom.

In this construction, instead of making the vane recesses or housings ofU form in cross section they are of rectangular section, an even numberconvenientlyfour such recesses being again provided, and arrangedsymmetrically around the periphery of the rotor; while each vanecomprises a blade 5| of rectangular section extending for the fulllength of the rotor and slidably mounted in each of the recesses orhousings so that the blades can move radially with respect thereto.

The peripheral face of each blade is formed with a longitudinal recess52 of circular form in which is mounted rotatabiy a roller 53 of alength equal to that of the recess and again adapted for rollingengagement with the adjacent surface of the stator, each blade androller forming together a complete vane.

Conveniently, the depth of each recess 52 is made somewhat lessthan thediameter of each roller, and the longitudinal edges of each recessextend towards one another so that. the rollers are retained in therecesses, although in order to reduce friction, they are maintained outof contact with the base of the recesses.

As in the preceding construction, the bases of opposite recesses 38 areconnected by circular passages 40 extending diametrically of the rotorand disposed at opposite ends thereof.

The diameter of these passages is slightly less than the width of theblades 5|, and the latter are each provided on their inner faces with aplunger 54 of circular form extending inwardly into the passages, thelength of each of these plungers being such that the opposed ends ofopposite plungers are spaced slightly apart for all positions of thepump stator within the housing.

With such an arrangement, as in the preceding construction, when duringthe rotation of the rotor a vane is forced inwardly of the rotor by theadjacent surface of the stator, the vane opposite thereto is forcedoutwardly by the fluid pressure between the opposed plungers and therollers are maintained continuously in contact with the stator duringthe rotation of the rotor.

In order to maintain the fluid pressure within the passages 40 duringthe continued rotation of the rotor, the forward side face of each bladeis provided with a semi-circular groove 55 disposed longitudinallythereof and communicating with a channel or passage 56 extendingcentrally of the plunger to the inner end thereof, each of these groovesbeing so disposed that they are in communication with the fluid withinthe stator during movement of the vanes from a suction to a deliveryport only, the inward movement of the blades 5| during the remainder ofsuch movement preventing the egress of the fluid during the passage ofthe vanes from the delivery to the suction port.

In this construction, the position of the stator within the housing, andhence the output of the pump is controlled by control gear comprising acontrol sleeve 51 mounted rotatabiy around the driving shaft II, thesleeve being provided at its rear end with a peripheral flange 58carrying a rearwardly extending pin 59 which engages a radiallyextending recess 60 formed in the adjacent face of the stator end disc49.

The forward end of the sleeve is provided with an operating lever GI,the arrangement being such that on moving the lever to pivot the sleeve,the stator is slidden transversely of the rotor to vary the quantity offluid delivered by the pump.

Alternatively, suitable cams may be provided for sliding the pump statoras in t e preceding construction.

Although I have described the pump rotors in both constructions as beingprovided with four vanes, it should be understood that in both forms ofthe apparatus any suitable even number of vanes may be employedaccording to the diameter of the pump rotor.

Referring now to Figures 6 to 11 of the drawings, the hydraulictransmission apparatus there illustrated comprises a rotary pump showngenerally at II 3, and a vane motor shown generally at II i disposedadjacent the end of the pump, the latter and the motor being containedin a common casing II comprising two pairs of horizontal side membersIIB of somewhat curved form, one pair being disposed above and the otherbeneath the pump and motor, and the individual members of each pairbeing connected by a central vertical partition plate II! which servesto separate the pump from the motor.

For closing the end of the casing, the latter is provided with endplates H8 and H9 of circular form and disposed respectively adjacent thepump and adjacent the motor.

The opposite sides of the casing are open as at I20, and the side edgesof the side members II6 are formed with vertical machined faces I2Iarranged for the detachable reception of transfer members I22 adapted totransfer the fluid from the pump to the motor and vice versa in a manherto be hereinafter described.

Extending longitudinally through the casing and supported from rollerbearings carried by the pump end plate H8 and by an annular bearingmember II Ia supported from the partition plate, is a main driving shaftI 23 for imparting the drive to the pump.

Adjacent the end plate IIO the driving shaft is provided with aperipheral flange I24 formed integrally therewith, while disposed aroundthe exterior of the shaft and extending from the end plate II8 to thepartition plate II! is a pump rotor I25 of annular form providedadjacent one end with an internal recess I26 of annular shape withinwhich is housed the periphery of the flange I2 3.

Conveniently, this flange is provided with a plurality of holes throughwhich extend longitudinally and into the rotor securing pins I21, tosecure the latter to the driving shaft.

The pump rotor I25 is provided with a plurality of longitudinallyextending peripheral recesses I28 of part circular form arrangedsymmetrically around the rotor, the base portions of such recessesadjacent the pump end plate being constituted also by arcuate slots I29formed in the periphery of the flange I24. Conveniently six suchrecesses are provided in the rotor.

Slidably and rotatably mounted in each of these recesses is a vane I 30of hollow cylindrical form which extends for the full length of therotor, and for preventing the oil or other fluid filling the interior ofthe vanes, the latter contain cork packing I30a.

Disposed within the pump portion of the easing and arranged above andbeneath the rotor are a pair of stator members I3I each of somewhatarcuate form which extend for the full width of the side members IIG,and-these members are of a thickness substantially less than thedistance between the periphery of the rotor and the adjacent innersurface of the side members, and are provided at their sides withvertical plane faces I32 which engage slidably corresponding facesformed on the adjacent surfaces of the two transfer members I22, so thateach stator member can slide in a vertical direction towards or awayfrom the surface of the rotor.

Conveniently, the inner face I33 of each stator member has a curvaturesimilar to that of the periphery of the rotor, so that each member canbe slidden in an inward direction until it is concentric with and inabutment with the rotor.

Extending longitudinally of the casing and between the front end plate II8 and the partition plate H1, is a pair of baflles I34 disposed one ateach side of the casing and centrally of the aforesaid opening I20.

The transverse section of each bafiie is of somewhat Wedge form, andthese are so arranged that their inner sides just make contact with theperiphery of the rotor and with the vanes during the rotation thereof,as will be apparent from Figure 6.

Each baflle is of such a depth that its upper andlower sides are spacedsomewhat from the adjacent sides of the stator members to provide aboveor beneath each bafile suction ports I35 and discharge ports I36, twopairs of ports each comprising a suction and a discharge port beingprovided one on each side of the rotor, the suction port of one pairbeing arranged diametrically opposite the suction port of the otherpair, and the delivery port of one pair being arranged similarly withrespect to its corresponding port in the other pair.

As in the case of the construction illustrated in Figures 1 to 3, theinterior of each stator member adjacent the ports is recessed somewhatas at I31, so that the fluid on admission to, or discharge from, thepump has a path which is substantially tangential to the periphery ofthe rotor.

In order to permit of relative movement between the stator members andthe baflies, while providing a continuous surface for the abutment ofthe vanes during their passage past the suction and delivery ports, theupper and lower sides of each ba'fiie are recessed at I38 and I39adjacent each end thereof as shown in Figure 9, and the sides of thestator members are provided adjacent the plates II! and II 8 withportions I40 which extend inwardly into these recesses as again shown inFigure 9.

The space between the said inwardly extending portions of each statormember provides the main opening of the suction and discharge ports, butto increase the area of these ports the sides of the baflle recesses I39adjacent the partition plate are inclined as shown at I 4|, suchinclination assisting also the movement of the fluid into and from thepump.

For maintaining the rotor vanes I30 in contact with the interior of thestator members and with the battles, for various positions of thesestator members in relation to the pump rotor, the main driving shaft I23is provided with a pair of spaced peripheral grooves I42 of semicircularsection disposed within the interior of the rotor, and the recesses I28containing nonadjacent vanes are connected to these grooves by openingsI43 extending radially through the annular rotor I25, and the groovesand the recesses are arranged to contain fluid so that when duringrotation one vane is forced inwardly of the rotor owing to theeccentricity of the stator member in relation thereto, the resultantfluid pressure produced forces the non-adjacent vanes outwardly thereofand maintains them incontact with the stator members and with thebaffles.

To maintain the grooves and recesses filled with fluid during thecontinued rotation of the rotor, the forward edge of each recess isprovided with grooves I44 corresponding to and arranged to function in amanner similar to the grooves 42 in the construction shown in Figures 1and 2.

The driving shaft I23 is provided with an extension I45 which projectsbeyond the motor end plate vI I9, and rotatably mounted upon thisextension is a sleeve I46 supportedfrom the extension I45 and from theend plate II9 by roller bearings I41 and I48 respectively.

Conveniently, the bearing I48 is carried by an annular bearing memberI49 supported from the plate II9.

Adjacent the end plate II9, the sleeve I46 is provided with a peripheralflange I50, and is I formed adjacent this flange with an annularextension I5I upon which is mounted a rotor I52 again of annular form,generally similar in. configuration to the pump rotor i25 and mounted inthe same manner. I

As in the case of the pump, the motor is provided with motor statormembers I53 of a form generally similar to the pump stator members andagain arranged above and beneath the rotor; but unlike the case of thepump, these members are stationary.

The motor rotor I52 is provided with'vanes I54 of a form similar to andhoused in the same manner as in the case of the pump vanes, but it ispreferred to guide the motor vanes and to maintain them in abutment withthe interior of the stator member by providing the adjacent surfaces ofthe bearing members III and I49 with recesses of somewhat oval form toprovide on each of these members cam faces I55 of a form correspondingto the configuration of the interior of the stator members and adaptedto engage each end of the vanes adjacent the inner side thereof tomaintain them in engagement with these members.

Since during rotation of the motor rotor a certain sliding movement mustoccur between the motor vanes and either the inner face of the statormembers or the cam faces if the vanes are simultaneously in contact withboth of these faces, it is preferred to provide means for maintainingthe vanes out of actual abutment with the cam faces during the normalworking of the apparatus.

For this purpose, the annular extension I5I of the sleeve I46 isprovided with a peripheral groove I56, while the rotor is groovedinternally at I56, and as in the case of the pump, the vane recesses areconnected to these grooves by openings I51, and the recesses andopenings are kept filled with fluid in a manner similar to the pump tomaintain the vanes in abutment with the inner face of the stator membersand out of contact with the cam faces I55.

In order to reduce the resistance to rotary movement of the motor vanes,these may be provided with a plurality of spaced peripheral grooves I5'Idisposed longitudinally of the vanes as shown in Figure 11.

Suitable oil seals I58 are provided for preventing the leakage of oilfrom the roller bearings of both the pump and the motor.

The motor is provided with bafiles I59 disposed in a manner similar tothe pump baflies; while the sides of the stator members I53 are providedsimilarly at their ends with inwardly extending portions I60 which sincethe motor stator members are stationary, abut the baffles and thusprovide a continuous surface for the engagement of the motor vanes.

In a manner similar to the pump, the baffles co-operate with theadjacent sides of the stator members to provide at opposite sides of themotor a pair of inlet and exhaust ports I6I and I62 respectively,corresponding to the suction and discharge ports of the pump.

Conveniently, the motor inlet ports I6I are arranged diagonally oppositeto the pump discharge ports I36, the motor exhaust ports I62 beingdisposed similarly with respect to the pump suction ports as shown inFigure 9, for a reason which will be hereinafter apparent.

In order to'provide a continuous circulation of the fluid through theapparatus, it is necessary that the pump discharge ports I36 should beconnected to the motor inlet ports IIII, and that the motor exhaustports I62 should be connected to the pump suction ports I35.

For this purpose the transfer members I22 are formed as castingsofhollow form provided on one side with a machined face I63 adapted forabutment with the adjacent face I2I and I64 of the side members H6 andbafiies I34 and I59 respectively, and each transfer member is formedwith a pair of internal passages I65 and I66, the passage I65 beingdisposed adjacent said machined face and the passage I66 remotetherefrom.

Each of these passages is of somewhat U form, the passage I65 being ofsubstantially circular section while the passage I66 is of elongatedsection. Each of the former passages is arranged to provide acommunication between the pump delivery ports I36 and the motor inletports I6I and thus serve as pressure chambers for connecting theseports, while each of the latter passages is arranged to provide acommunication between the motor exhaust ports I62 and pump suction portsI35, and thus provide a suction chamber for connecting these latterports.

Thus, fluid is admitted from each suction chamber I66 through thesuction ports I35 to opposite sides of the pump rotor, is swept by thepump rotor vanes co-operating with the adjacent stator member to thefollowing discharge port, and is deflected therethrough by the adjacentbafile and by the engagement of the latter with the periphery of thepump rotor or vanes thereof, and in a direction which is somewhattangential to the exterior of the rotor.

The fluid now under a considerable pressure is forced through the pumpdischarge ports I36 into each pressure chamber I65, and passes therefromthrough the motor inlet ports I6I into the motor, and is forced againstthe vanes on opposite sides of the motor rotor, being again similarlydeflected by the motor bafiles I59 through the motor exhaust ports I62back into the suction chambers I66.

Thus a continuous circulation of the fluid from the pump to the motorand back again is set up, while by arranging the pump discharge portsdiagonally opposite to the motor inlet ports, and the motor exhaustports diagonally opposite to the pump suction ports, any sudden changein the-direction of the fluid during its passage from the pump to themotor and back is avoided so that hydraulic losses are reduced to aminimum, while the motor rotor is driven inthe same direction as thedirection of rotation of the pump rotor.

Further, by admitting the fluid to opposite sides of the pump and motorrotors, the work done on opposite sides of each rotor is substantiallyequal and no unbalanced transverse pressure is applied to the rotors, sothat the whole apparatus is mechanically and hydraulically balane :d,

Again, by admitting the fluid to opposite sides of the rotors usefulwork is performed on both sides of the pump and motor, and in fact theamount of work done with an apparatus constructed as shown in Figures 6to 11 of the drawings is approximately twice that performed withconstruction of substantially the same size wherein the pump and motorare each provided with a single fluid supply and discharge port in whichuseful work is done by or on one half only of the respective rotors.

Again, by disposing the bafiles so that the whole of the fluid isexpelled through the discharge or exhaust ports as the case may be, nowasteful work is done by circulating the liquid around the interior ofthe pump or motor, and the efliciency of the apparatus as a whole isenhanced.

Suitable control means are provided for varying the position of eachstator member in relation to the pump rotor and thus to vary the volumeswept out by a vane during a given revolution of the rotor and hence thevolume of the fluid delivered from the pump to the motor during suchrevolution.

Conveniently such control means comprise the provision on the medialpart of each stator member of a bracket I61 extending outwardlytherefrom, and which is slidable in a suitable opening provided in theadjacent side member I I6, and the free end of each bracket is connectedpivotally to one end of a lever I68, the opposite end of the lever beingsupported from a spindle I69 supported pivotally upon a pair of lugs I10carried by the adjacent side member, the spindle being provided with afurther lever I1I extending oppositely to the lever I68, and each ofthese levers I1I are connected pivotally at their free ends to one of apair of screws I12 and I13 which extend towards one another, the formerscrew having a, right hand thread and the latter a left hand thread,each thread being of the same pitch and being connected by a commonturn-buckle I14 which is adapted to be rotated from suitable operatingmeans not shown in the drawings.

As will be apparent on rotating the turn-buckle, the screws are moved inopposite directions to slide the two stator members I3I towards or awayfrom the rotor by an equal amount, so that the work done on each side ofthe rotor is equal for all positions of the stator members in relationto the rotor and consequently for all variations in the amount of powertransmitted from the pump to the motor.

Further, by admitting the fluid to opposite sides of the rotor, the workdone by the co-operation of the vanes and stator member is equal foreach stator member, so that the fluid pressure on the interior of thestator members which tends to move these in an outward direction, isequal for each member, and by connecting the latter by control gear inthe manner described the fluid pressure on the two stator members iscounterbalanced and there is no resultant tendency for the statormembers to move transversely of the rotor as in the case withconstructions such as those shown in Figures 1 to 5 wherein more work isdone on one side of the rotor to produce a nection to suitable resultantfluid pressure tending to move the stator member into a position inwhich it is concentric with the rotor.

Further, in the arrangement illustrated in Figures 6 to 11 of thedrawings, the two stator members can be slidden from a position in whichthey are displaced by a maximum distance from the periphery of the pumprotor, and the quantity of fluid delivered by the pump to the motor fora given rotation of the rotor is at a maximum and the greatest amount ofpower under maximum load conditions is transmitted by the apparatus, toa position in which they are adjacent the periphery of the rotor,wherein no fluid is delivered to the motor and no power is transmittedby the apparatus, the latter being thus in neutral gear.

Thus, a considerable variation may be obtained in the amount of powertransmitted.

If desired a still further variation may be obtained by constructing themotor stator members in a manner exactly similar to the pumpstator'members and arranging them for movement towards or away from themotor rotor, similar control means being provided as in the case of thepump. With such an arrangement the cam faces I55 are omitted, and themeans for maintaining the vanes in engagement with the interior of thestator members may be exactly similar to that employed in the case ofthe pump.

As will be apparent, when the pump stator members I3I are adjacent theperiphery of the pump rotor, the fluid is expelled almost completelyfrom the pump, and in order to enable the fluid readily to fill the pumpwhen it is desired to again reach normal output, quickly, the transfermembers are each apertured as at I15 and provided with nipples I16adapted for conpipes which serve to supply fluid from a reservoir notshown in the drawings to the suction chambers I66 and hence to theinterior of the pump.

In order that the direction of rotation of the motor rotor canbereversed with respect to the pump rotor, as for instance when theapparatus is employed as an infinitely variable gear for mechanicallypropelled vehicles, means may be provided for reversing the direction offlow of the fluid through the motor.

For this purpose, each of the transfer members I22 is, as shown inFigures 12 to 14, made of hollow cylindrical form with the central axisthereof disposed longitudinally of the apparatus and parallel to theaxis of rotation. of the pump and motor rotors, the transfer membersbeing again provided with peripheral flanges which are bolted to theadjacent side members II6 of the casing.

Mounted within each of the transfer members is a reversing valve I11 ofcylindrical form adapted for rotation about an axis parallel to the axisof rotation of the rotors and provided at one end with an operatingspindle I18 which projects through a cover plate I19 which serves tosecure the valve within thetransfer member.

Each of these reversing valves is formed internally at one side thereofwith pressure and suction chambers I65 and I66 respectively and of aform similar to the pressure and suction chambers of the precedingconstruction and again adapted to provide respectively a communicationbetween the pump delivery and motor inlet ports and between the motorexhaust and pump suction ports with the valve in the position shown inFigure 12.

Formed in the opposite side of each reversing valve is a pair of spacedreverse ports I80 of substantially U form and arranged with their planesparallel to the axis of rotation of the valve and each of these ports isadapted on movement of the valve through 180 to provide communicationbetween a pump delivery port I36 and motor exhaust port I62 or between amotor inlet port I6! and a pump suction port I35.

In this latter position of the valve, the fluid is admitted to anddischarged from the motor through the motor exhaust and inlet portsrespectively, so that the direction of flow of the fluid through themotor is reversedwith consequent reversal of the direction of rotationof the motor rotor I52.

In order that the fluid may be again supplied readily to the pump afterthe apparatus has been in the neutral position with the stator membersI3I in abutment with the periphery of the pump rotor, each valve isprovided with a fluid supply passage I8I extending diametricallytherethrough and adapted with the valves in the position shown toprovide a communication between each of the suction chambers I66 and asuitable nipple I16 provided on the exterior of each transfer member andadapted as in the-previous construction,

for connection to a suitable fluid supply reservoir not shown in thedrawings.

With the valve in the reverse position, the end of the supply passageI8I is closed by the seating thereof on the medial part I82 of thetransfer member adjacent the baffles.

Any suitable control gear may be provided for rotating the two reversingvalves simultaneously and by an equal movement to reverse at oneoperation the direction of flow of the fluid at both sides of the motorrotor.

The fluid employed for transmitting the power from the pump to the motoris preferably oil, although other suitable fluids may be used.

The apparatus is adapted to transmit the POW- er to a driven shaft atI83 and in order that this shaft may be driven at the same speed as thedriving shaft I23, while at the same time unnecessary wear of thetransmission apparatus may be avoided under such conditions, clutchmeans, shown generally at I84 are provided for alternatively placing thedriven member in direct engagement with an extension I85 of the drivingshaft or with an annular extension I86 of the rotor member I46 which isprovided with clutch dogs I81 for this purpose. Thus, the shaft I83 maybe driven at the same speed as the driving shaft I23 and in thedirection of rotation of the latter, or an infinitely variable drive maybe imparted to the driven shaft which may be rotated in either directionrelative to the driving shaft.

It should, however, be understood that such clutch means forms no partof the invention forming the subject of the present application.

If desired in order to maintain a fluid-tight connection between thepump stator members, and in addition the motor stator members if thelatter are movable, and the adjacent surfaces of the transfer members orof the plates H1, H8, H9, these surfaces or the surfaces of the statormembers may be provided with sealing means similar to that shown at 36in the construction illustrated in Figure 1; such arrangement with thisconstruction obviating the necessity to machine accurately theco-operating surfaces.

As will be apparent from Figure 8, the motor end plate H9 is spaced fromthe partition plate III by a distance less than the spacing off thelatter from the pump end plate II8, while the length of the motor statormembers and motor vanes is less than the length of the correspondingpump members, although the radial dimensions of these members and of thetwo rotors are similar.

With such an arrangement, the motor rotor is driven at a speedsubstantially greater than that of the pump rotor, and is particularlysuitable in cases where the apparatus is employed for transmitting powerfrom a slow running oil engine, but it should of course be understoodthat the length of the said motor members may be made equal to orgreater than that of the corresponding pump .members according to thespeed of the driving shaft and to the speed at which it is desired totransmit the power. For instance, the length of the motor members may beconsiderably greater than that of the corresponding pump members wherethe power is obtained from a high speed petrol engine.

Such changes in gear ratio may of course be obtained also by alteringthe respective radial dimensions of the pump and rotor members to varythe ratio of the swept volumes of the pump and motor as required.

Although I have described the invention as being applied to a rotarypump and a vane motor combined to provide apparatus for the hydraulictransmission of power it is understood that the invention is equallyapplicable to a pump which is unprovided with a motor and employed forany purpose where it is desired to vary the hydraulic head of thedelivered fluid, or, alternatively, it may be applied to a vane motor,blower or exhauster wherein no pump is provided, and it is desired tovary the mechanical output of such an engine, the fluid being suppliedfrom any suitable external source.

Further, the vanes of the form shown in Figures 4 and 5, may be employedin the construc tion shown in Figures 6 to 14, while instead ofproviding the pump and motor rotors with six vanes it should-beunderstood that any suitable even number of vanes may be employedaccording to the diameter of the rotors.

I claim: I

1. In a rotary engine, stator and rotor members, said rotor having aplurality of recesses extending substantially in the direction of itsaxis of rotation, vanes of cylindrical form rotatable in said recessesand adapted for rolling engage- -ment with the adjacent surface of thestator member, said vanes being movable inwardly and outwardly of saidrecesses, said stator surface being eccentric in relationto said rotor,said engine having a cam face concentric in relation to said statorsurface but spaced therefrom, said cylindrical vanes extending betweensaid cam face and stator surface and having a diameter slightly lessthan the distance between said cam face and stator surface, and meansfor maintaining said vanes out of actual contact with the cam face andin rolling engagement with said,

rotor, said engine having a cam face concentric in relation to saidstator surface but spaced therefrom, said cylindrical vanes extendingbetween said cam face and stator surface and having a diameter slightlyless than the distance between said cam face and'stator surface, saidrotor having passages adapted to supply fiuid under pressure from saidengine to the bases of said recesses and maintain said vanes out ofactual contact with the cam face and in rolling engagement with saidstator surface during the rotation of the rotor.

I aim a rotary engine, stator and rotor members, said rotor having aplurality of recesses extending substantially in the direction of itsaxis of rotation, vanes of cylindrical form rotatable in said recessesand adapted for rolling engagement with the adjacent surface of thestator member, means for supplying fluid to said vanes and fordischarging said fluid from the engine, said stator surface beingeccentric in relation to the adjacent surface of the rotor member, saidstator and rotor being relatively displaceable to vary saideccentricity, said eccentric stator surface being adapted during therotation of the rotor to permit of some vanes moving outwardly inrelation to their recesses and others simultaneously moving inwardly inrelation to their recesses to an extent dependent on said eccentricity,each of said vane recesses having in one side wall thereof a grooveextending from the edge of the recess towards the base thereof, each ofsaid grooves being capable of feeding fluid under pressure from theinterior of said engine to the base of the vane recess, said rotorhaving passages of substantial cross section connecting recesses ofoutwardly moving vanes to recesses of simultaneously inwardly movingvanes, said grooves having a length substantially less than the diameterof the adjacent cylindrical vane, said vanes for various relativedisplacements of the stator and rotor members being adapted in theirinnermost positions in relation to their recesses to close thecommunication provided by said grooves between the interior of theengine and the vane recesses, and in their outermost positions inrelation to their housings to open such communications and permit offluid under pressure being fed to the recesses.

EDWARD EWART GUINNESS.

